CA2025756A1 - Heat exchanger for the cooling of reaction gas - Google Patents
Heat exchanger for the cooling of reaction gasInfo
- Publication number
- CA2025756A1 CA2025756A1 CA 2025756 CA2025756A CA2025756A1 CA 2025756 A1 CA2025756 A1 CA 2025756A1 CA 2025756 CA2025756 CA 2025756 CA 2025756 A CA2025756 A CA 2025756A CA 2025756 A1 CA2025756 A1 CA 2025756A1
- Authority
- CA
- Canada
- Prior art keywords
- tube
- heat exchanger
- tubes
- gas
- cooling
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
- F28D7/0075—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the same heat exchange medium flowing through sections having different heat exchange capacities or for heating or cooling the same heat exchange medium at different temperatures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1669—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
- F28D7/1676—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube with particular pattern of flow of the heat exchange media, e.g. change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0075—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for syngas or cracked gas cooling systems
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
ABSTRACT
A heat exchanger for the cooling of cracking gas produced in a tube furnace includes a cooled single tube which is directly connected to at least one tube of the tube furnace. The single tube is connected with a plurality of tubes of a tube bundle heat exchanger through a distribution chamber. An outer tube surrounds the single tube and is connected to an outer mantle which surrounds the tube bundle. The outer tube and the outer mantle are provided with a coolant supply union and a coolant discharge union respectively. The cooled single tube and the tube bundle heat exchanger are combined in a single heat exchanger, providing for lower pressure loss and construction cost whilst maintaining favourable processing and cooling conditions.
A heat exchanger for the cooling of cracking gas produced in a tube furnace includes a cooled single tube which is directly connected to at least one tube of the tube furnace. The single tube is connected with a plurality of tubes of a tube bundle heat exchanger through a distribution chamber. An outer tube surrounds the single tube and is connected to an outer mantle which surrounds the tube bundle. The outer tube and the outer mantle are provided with a coolant supply union and a coolant discharge union respectively. The cooled single tube and the tube bundle heat exchanger are combined in a single heat exchanger, providing for lower pressure loss and construction cost whilst maintaining favourable processing and cooling conditions.
Description
7 ~ ~
HEAT EXCI~UNGER FOR THE COOLING OF REACTION GAS
The invention relates to a heat exchanger for the cooling of reaction gas. In particular, the invention relates to heat exchangers used for quickly cooling reaction gases from, for example, cracking furnaces and reactors in industrial operations.
To attain the highest possible cracking yield, hot cracking ~as which exits a tube furnace (the type of furnace mostly used in cracking operations) must be cooled as quickly as possible to an intermediate temperature at which the chemical reactions taking place in the cracking gas are inhibited. Further cooling of the cracking gas to an appropriate end temperature may be carried out more gradually in consideration of other technical process and economic criteria. Small total pressure loss in the gas has a large impact on the yield of the reaction. Thus, for economic reasons, a physically short overall construction is desirable.
:.;
In prior art apparatus such as disclosed in British patent GB 10 87 512, cracking gas is cooled to the end temperature in a single tube which is directly connected to an exit of the furnace. Such a construction guarantees fast cooling of the gas, but in consequence, considerable pressure loss must be accepted. That reference teaches the method of carrying out the cooling in two steps. In the first step the gas is cooled as ~uickly as possible to the desired intermediate temperature within the single cooled tube. ~ubsequently, the cracking gas is transported through interconnecting conduits to a second separate apparatus wherein the second step of the cooling ls realized. The construction costs of such an arrangement which requires two separate individual pieces of apparatus are very high. The interconnecting conduits between the two pieces cause a high pressure loss,,which lowe,rs the reaCtion yield.
It is further known in the art to connect a plurality of furnace exits to a heat exchanger entry chamber and to distribute the cracking gas from the entry chamber into a plurality of cooling tubes. A disadvantage of such an arrangement is that the velocity of the reaction gas becomes slower - 1 - , PAT 159~0-1 ~2~7~
.. ..
, at the entry chaMber by reason of its larger volume. As a result, cooling of the gas after leaving the furnace is delayed, which reduces the reaction yield. Cooling of the gas is in fact even further delayed, since the entry chamber is not cooled.
s It is an ob~ect of the disclosure to reduce the construction costs of such a heat exchanger while providing favourable processing and cooling condltions.
Here described in a heat exchanger including first and second cooling arrangements which are integrally enclosed for containment of the cooling medium. Thus, both cooling arrangements are combined into a single apparatus, which reduces construction costs. The fast cooling of the reaction gas to the intermediate temperature in the first cooling arrangement commences immediately after the furnace exit and without reduction in the gas velocity. The final cooling in the directly integrated second cooling arrangement is achieved at low mass speed and, therefore, with small pressure loss. As a result, the second cooling arrangement may ~ i be much shorter than a single cooled tube. The distribution chamber between 20 the first and the second cooling arrangement may also be cooled and thus ~
contribute to the heat exchange. In a preferred embodiment, conical -construction of the distribution chamber provides for efficient pressure recovery and, therefore, a smaller total pressure loss.
Embodiments of the invention will now be described by way of example only with reference to the accompanying drawings, wherein, ~ -Fig. 1 is a schematic axial cross-section through a heat exchanger embodying the invention for the cooling of reaction gas; and Fig. 2 is a schematic axial cross-section through a preferred embodiment of the heat exchanger shown in Fig. 1.
The illustrated heat exchangers are used for the quick cooling of cracking gas or any other reaction gas, which is produced in a furnace ~.~
20257~6 constructed as a tube furnace or in a reactor of a chemical plant. A tube furnace (not illustrated) generally includes a plurality of separately heated tubes through which the reaction gas streams. The heat exchanger as illustrated in Fig. 1, includes two cooling arrangements, the first being constructed as a single tube heat exchanger 20 having a single tube 1, and the second being constructed as a tube bundle heat exchanger 30 having tubes 2. Single tube 1 is surrounded by an outer tube 3 and is, at its gas entry end, sealingly connected with that outer tube 3 through an annular flange 4. Single tube 1 directly communicates with a heated tube of the tube furnace through a thermal stress free connection (not illustrated). The inner dimensions of the heated tube and of single tube 1 are substantially the same.
The gas exit end of single tube 1 opens into a distribution chamber 5 which is defined at its far axial end by a first tube end plate 6. The gas entry ends of tubes 2 of tube bundle heat exchanger 30 are welded to the first tube end plate 6 to produce a gas tight connection. A second tube end plate 7 is affixed to the gas exit ends of tubes 2, the connection also being gas tight. A gas exit chamber ô is positioned downstream and adjacent the second tube end plate 7 for removal of cold cracking gas. An outer mantle 9 surrounds tubes 2 thereby defining an inner chamber 10, In the heat exchanger illustrated in Fig. 1, distribution chamber 5 has a conical cross-section and its diameter increases in the direction of flow of the cracking gases from that of single tube 1 to the diameter of first tube end plate 6. This end plate 6, which partly defines distribution cbamber 5, has a smaller diameter than the inner diameter of outer mantle 9. Outer tube 3 is connected with outer mantle 9 through a conical intermediate member 11 in the region of distribution chamber 5. Intermediate member 11 provides for connection between an annular space 12, which is radially defined by and located between single tube 1 and outer tube 3, and chamber 10 which is radially defined by outer mantle 9 and single tube 1, so that coolant may continuously flow through the zone which comprises both space 10 and then chamber 12. As a result, intermediately located distribution chamber 5 is also located within the coolant stream and may thus be used for the cooling of the cracking gas.
HEAT EXCI~UNGER FOR THE COOLING OF REACTION GAS
The invention relates to a heat exchanger for the cooling of reaction gas. In particular, the invention relates to heat exchangers used for quickly cooling reaction gases from, for example, cracking furnaces and reactors in industrial operations.
To attain the highest possible cracking yield, hot cracking ~as which exits a tube furnace (the type of furnace mostly used in cracking operations) must be cooled as quickly as possible to an intermediate temperature at which the chemical reactions taking place in the cracking gas are inhibited. Further cooling of the cracking gas to an appropriate end temperature may be carried out more gradually in consideration of other technical process and economic criteria. Small total pressure loss in the gas has a large impact on the yield of the reaction. Thus, for economic reasons, a physically short overall construction is desirable.
:.;
In prior art apparatus such as disclosed in British patent GB 10 87 512, cracking gas is cooled to the end temperature in a single tube which is directly connected to an exit of the furnace. Such a construction guarantees fast cooling of the gas, but in consequence, considerable pressure loss must be accepted. That reference teaches the method of carrying out the cooling in two steps. In the first step the gas is cooled as ~uickly as possible to the desired intermediate temperature within the single cooled tube. ~ubsequently, the cracking gas is transported through interconnecting conduits to a second separate apparatus wherein the second step of the cooling ls realized. The construction costs of such an arrangement which requires two separate individual pieces of apparatus are very high. The interconnecting conduits between the two pieces cause a high pressure loss,,which lowe,rs the reaCtion yield.
It is further known in the art to connect a plurality of furnace exits to a heat exchanger entry chamber and to distribute the cracking gas from the entry chamber into a plurality of cooling tubes. A disadvantage of such an arrangement is that the velocity of the reaction gas becomes slower - 1 - , PAT 159~0-1 ~2~7~
.. ..
, at the entry chaMber by reason of its larger volume. As a result, cooling of the gas after leaving the furnace is delayed, which reduces the reaction yield. Cooling of the gas is in fact even further delayed, since the entry chamber is not cooled.
s It is an ob~ect of the disclosure to reduce the construction costs of such a heat exchanger while providing favourable processing and cooling condltions.
Here described in a heat exchanger including first and second cooling arrangements which are integrally enclosed for containment of the cooling medium. Thus, both cooling arrangements are combined into a single apparatus, which reduces construction costs. The fast cooling of the reaction gas to the intermediate temperature in the first cooling arrangement commences immediately after the furnace exit and without reduction in the gas velocity. The final cooling in the directly integrated second cooling arrangement is achieved at low mass speed and, therefore, with small pressure loss. As a result, the second cooling arrangement may ~ i be much shorter than a single cooled tube. The distribution chamber between 20 the first and the second cooling arrangement may also be cooled and thus ~
contribute to the heat exchange. In a preferred embodiment, conical -construction of the distribution chamber provides for efficient pressure recovery and, therefore, a smaller total pressure loss.
Embodiments of the invention will now be described by way of example only with reference to the accompanying drawings, wherein, ~ -Fig. 1 is a schematic axial cross-section through a heat exchanger embodying the invention for the cooling of reaction gas; and Fig. 2 is a schematic axial cross-section through a preferred embodiment of the heat exchanger shown in Fig. 1.
The illustrated heat exchangers are used for the quick cooling of cracking gas or any other reaction gas, which is produced in a furnace ~.~
20257~6 constructed as a tube furnace or in a reactor of a chemical plant. A tube furnace (not illustrated) generally includes a plurality of separately heated tubes through which the reaction gas streams. The heat exchanger as illustrated in Fig. 1, includes two cooling arrangements, the first being constructed as a single tube heat exchanger 20 having a single tube 1, and the second being constructed as a tube bundle heat exchanger 30 having tubes 2. Single tube 1 is surrounded by an outer tube 3 and is, at its gas entry end, sealingly connected with that outer tube 3 through an annular flange 4. Single tube 1 directly communicates with a heated tube of the tube furnace through a thermal stress free connection (not illustrated). The inner dimensions of the heated tube and of single tube 1 are substantially the same.
The gas exit end of single tube 1 opens into a distribution chamber 5 which is defined at its far axial end by a first tube end plate 6. The gas entry ends of tubes 2 of tube bundle heat exchanger 30 are welded to the first tube end plate 6 to produce a gas tight connection. A second tube end plate 7 is affixed to the gas exit ends of tubes 2, the connection also being gas tight. A gas exit chamber ô is positioned downstream and adjacent the second tube end plate 7 for removal of cold cracking gas. An outer mantle 9 surrounds tubes 2 thereby defining an inner chamber 10, In the heat exchanger illustrated in Fig. 1, distribution chamber 5 has a conical cross-section and its diameter increases in the direction of flow of the cracking gases from that of single tube 1 to the diameter of first tube end plate 6. This end plate 6, which partly defines distribution cbamber 5, has a smaller diameter than the inner diameter of outer mantle 9. Outer tube 3 is connected with outer mantle 9 through a conical intermediate member 11 in the region of distribution chamber 5. Intermediate member 11 provides for connection between an annular space 12, which is radially defined by and located between single tube 1 and outer tube 3, and chamber 10 which is radially defined by outer mantle 9 and single tube 1, so that coolant may continuously flow through the zone which comprises both space 10 and then chamber 12. As a result, intermediately located distribution chamber 5 is also located within the coolant stream and may thus be used for the cooling of the cracking gas.
2~2~7~6 .,' The preferred coolant used is highly pressurized water which is supplied to the heat exchanger through one or more coolant supply unions 13. The water is partially vapourized by the transfer of heat from the cracking gas, which streams through single tube 1 distribution chamber 5 and tubes 2, and exits through one or more coolant discharge unions 14 as a water/steam mixture. Supply union 13 is mounted to outer tube 3 and discharge union 14 to outer mantle 9.
In the heat exchanger shown in Fig. 2, single tube 1' and tubes 2' are mounted in a parallel arrangement within outer mantle 9', with tube 1 mantle 9' preferably co-axial. Distribution chamber 5' is defined by first ;
tube end plate 6' and a hood 15 for redirecting the reaction gas stream which are both mounted on and sealingly close one end of outer mantle 9'.
Second tube end plate 7' is positioned at the gas exit end of tubes 2' and secured to outer mantle 9' and to outer tube 3' at its end remote from first tube end plate 6'. Outer tube 3', in this embodiment, surrounds single tube 1' for only part of its length. Outer tube 3' is over at least part of its axial extent surrounded by an annular gas collecting chamber 16, which includes a gas exit spigot 17 and is defined in the axial direction of outer tube 3', by second tube end plate 7' separating chamber 16 from chamber 10' and by an end wall 22 remote from second tube end plate 7', and in the radial direction by outer mantle 9'.
In contrast to the heat exchanger shown in Fig. 1, wherein the cracking gas to be cooled flows through single tube 1 and tubes 2 with no change in the flow direction, in the heat exchanger as shown in Fig. 2, the gas flows through single tube 1' and tubes 2' in a counterflow arrangement.
In a heat exchanger as shown in Fig. 2, annular space 12' and chamber 10' are, like the embodiment shown in Fig. 1 for space 12 and chamber 10, connected so that the same coolant may continuously flow through the coolant zone which they define. Supply union 13' for the coolant is mounted to outer tube 3' close to the gas entry end of the heat exchanger, and discharge union 14' is secured to outer mantle 9' adjacent first tube end plate 6'.
~Q2~7~g ` ~- ~
: :~
The cracking gas G produced in the tube furnace flows into gas entry end 21, 21' of single ~ube 1, 1' of single tube heat exchanger 20, 20' as indicated by the solid arrow, which single tube represents the first cooling arrangement, for cooling at constant cross section and without significant velocity reduction. Immediately as the cracking gas exits the tube furnace, its heat starts to be transferred to the coolant C which enters the heat exchanger through coolant supply union 13 and which then flows to annular space 12, 12' which surrounds single tube 1, 1'. The cracking gas can thus be cooled quickly to the required intermediate temperature at a high mass speed. The gas exits from single tube 1, 1' directly into distribution chamber 5, 5', which by allowing velocity reduction permits conversion of dynamic energy to pressure energy from the Bernoulli effect and provides for regaining of pressure and thus reduction of the total pressure loss. From distribution chamber 5, 5', the intermediate temperature cracking gas enters 15 directly into tubes 2, 2' of tube bundle heat exchanger 30, 30' which represents the second cooling arrangement. The cracking gas flows through these tubes 2, 2' with a lower mass speed and therefore with a desired reduced pressure loss. The remaining heat in the cracking gas is transferred to the surrounding coolant within chamber 10, 10', which allows cooling to a selected end temperature. The heated coolant exits the heat exchanger through coolant discharge union 14, 14' and the gas at the selected end temperature leaves through gas exit chamber 8 of the embodiment shown in Fig. 1 or through gas exit spigot 17 of the embodiment shown in - -Fig. 2.
In the heat exchanger shown in Fig. 2, single tube 1' and tubes 2' are mounted in a parallel arrangement within outer mantle 9', with tube 1 mantle 9' preferably co-axial. Distribution chamber 5' is defined by first ;
tube end plate 6' and a hood 15 for redirecting the reaction gas stream which are both mounted on and sealingly close one end of outer mantle 9'.
Second tube end plate 7' is positioned at the gas exit end of tubes 2' and secured to outer mantle 9' and to outer tube 3' at its end remote from first tube end plate 6'. Outer tube 3', in this embodiment, surrounds single tube 1' for only part of its length. Outer tube 3' is over at least part of its axial extent surrounded by an annular gas collecting chamber 16, which includes a gas exit spigot 17 and is defined in the axial direction of outer tube 3', by second tube end plate 7' separating chamber 16 from chamber 10' and by an end wall 22 remote from second tube end plate 7', and in the radial direction by outer mantle 9'.
In contrast to the heat exchanger shown in Fig. 1, wherein the cracking gas to be cooled flows through single tube 1 and tubes 2 with no change in the flow direction, in the heat exchanger as shown in Fig. 2, the gas flows through single tube 1' and tubes 2' in a counterflow arrangement.
In a heat exchanger as shown in Fig. 2, annular space 12' and chamber 10' are, like the embodiment shown in Fig. 1 for space 12 and chamber 10, connected so that the same coolant may continuously flow through the coolant zone which they define. Supply union 13' for the coolant is mounted to outer tube 3' close to the gas entry end of the heat exchanger, and discharge union 14' is secured to outer mantle 9' adjacent first tube end plate 6'.
~Q2~7~g ` ~- ~
: :~
The cracking gas G produced in the tube furnace flows into gas entry end 21, 21' of single ~ube 1, 1' of single tube heat exchanger 20, 20' as indicated by the solid arrow, which single tube represents the first cooling arrangement, for cooling at constant cross section and without significant velocity reduction. Immediately as the cracking gas exits the tube furnace, its heat starts to be transferred to the coolant C which enters the heat exchanger through coolant supply union 13 and which then flows to annular space 12, 12' which surrounds single tube 1, 1'. The cracking gas can thus be cooled quickly to the required intermediate temperature at a high mass speed. The gas exits from single tube 1, 1' directly into distribution chamber 5, 5', which by allowing velocity reduction permits conversion of dynamic energy to pressure energy from the Bernoulli effect and provides for regaining of pressure and thus reduction of the total pressure loss. From distribution chamber 5, 5', the intermediate temperature cracking gas enters 15 directly into tubes 2, 2' of tube bundle heat exchanger 30, 30' which represents the second cooling arrangement. The cracking gas flows through these tubes 2, 2' with a lower mass speed and therefore with a desired reduced pressure loss. The remaining heat in the cracking gas is transferred to the surrounding coolant within chamber 10, 10', which allows cooling to a selected end temperature. The heated coolant exits the heat exchanger through coolant discharge union 14, 14' and the gas at the selected end temperature leaves through gas exit chamber 8 of the embodiment shown in Fig. 1 or through gas exit spigot 17 of the embodiment shown in - -Fig. 2.
Claims (5)
1. A heat exchanger for the cooling of reaction gas produced in a tube furnace comprising, a cooled single tube, an outer tube surrounding said single tube, a distribution chamber, a tube bundle, and an outer mantle surrounding said tube bundle;
said single tube communicating at one end with at least one of a plurality of tubes of said tube furnace, and, at its other end through said distribution chamber, with at least one tube of said tube bundle, said outer tube and said outer mantle being interconnected to define a coolant flow zone therethrough and a coolant supply union and a coolant discharge union respectively for said zone.
said single tube communicating at one end with at least one of a plurality of tubes of said tube furnace, and, at its other end through said distribution chamber, with at least one tube of said tube bundle, said outer tube and said outer mantle being interconnected to define a coolant flow zone therethrough and a coolant supply union and a coolant discharge union respectively for said zone.
2. A heat exchanger as defined in claim 1, wherein said outer tube of said single tube is connected with said outer mantle adjacent said distribution chamber.
3. A heat exchanger as defined in claim 1 or 2, wherein said distribution chamber flares conically outwards in flow direction of said reaction gas and is partly defined by a first tube end plate which is pierced by gas entry ends of the tubes of said tube bundle and has a diameter which is smaller than an inner diameter of said outer mantle.
4. A heat exchanger as defined in claim 1, wherein said single tube extends within said outer mantle parallel to the tubes of said tube bundle, permitting said reaction gas to flow through the tubes of said tube bundle and said single tube in a counterflow arrangement, and said outer tube being connected to said outer mantle at a second tube end plate pierced by gas exit ends of said tubes of said tube bundle.
5. A heat exchanger as defined in claim 1 or 4, wherein said at least one tube of said tube furnace has the same inner diameter as said single tube connected thereto.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3931685.8 | 1989-09-22 | ||
| DE19893931685 DE3931685A1 (en) | 1989-09-22 | 1989-09-22 | HEAT EXCHANGER FOR COOLING REACTION GAS |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2025756A1 true CA2025756A1 (en) | 1991-03-23 |
Family
ID=6389997
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2025756 Abandoned CA2025756A1 (en) | 1989-09-22 | 1990-09-19 | Heat exchanger for the cooling of reaction gas |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0418534A3 (en) |
| JP (1) | JPH03113291A (en) |
| CA (1) | CA2025756A1 (en) |
| DE (1) | DE3931685A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2134736B1 (en) * | 1997-08-11 | 2000-05-16 | Milla Carlos Santaolalla | REFRIGERATION SYSTEM FOR LIQUIDS. |
| ITMI20051834A1 (en) * | 2005-09-30 | 2007-04-01 | Eni Spa | HEAT EXCHANGER |
| JP5180716B2 (en) * | 2008-04-08 | 2013-04-10 | サンデン株式会社 | Heat exchanger and hot water supply apparatus using the same |
| JP5910663B2 (en) * | 2010-04-09 | 2016-04-27 | 株式会社デンソー | Exhaust heat exchanger |
| JP5904108B2 (en) | 2011-12-19 | 2016-04-13 | 株式会社デンソー | Exhaust heat exchanger |
| DE102012017405A1 (en) * | 2012-09-03 | 2014-03-06 | GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) | Heat exchanger for motor vehicle-air conditioning system of motor vehicle, has two inner tubes and outer tube which partially encloses inner tube under formation of intermediate space flowed through by heat exchanging medium |
| CN103256835B (en) * | 2013-05-17 | 2015-07-29 | 广西壮族自治区特种设备监督检验院 | A kind of shell-and-tube heat exchanger facilitating cleaning in shell-side |
| EP2814144A1 (en) * | 2013-06-10 | 2014-12-17 | ABB Technology AG | An air-to-air heat exchanger |
| CN111964489B (en) * | 2020-08-17 | 2021-10-22 | 博瑞特热能设备股份有限公司 | High-efficiency heat exchanger capable of improving differentiation of cross sectional areas among different heat exchange tubes |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1015021B (en) * | 1954-02-19 | 1957-09-05 | Atlas Werke Ag | Heat exchanger |
| DE2037382A1 (en) * | 1970-07-23 | 1972-02-03 | Bbc Sulzer Turbomaschinen | Double walled heat exchanger - with continuous cooling flow through wall space at hot end |
| FR2429402A1 (en) * | 1978-06-22 | 1980-01-18 | Commissariat Energie Atomique | INTERMEDIATE EXCHANGER FOR FAST NEUTRAL NUCLEAR REACTOR |
| EP0008633B1 (en) * | 1978-07-10 | 1981-12-09 | Linde Aktiengesellschaft | Heat exchanger for high-pressure and high-temperature use, process for its manufacture, and use as a reactor |
-
1989
- 1989-09-22 DE DE19893931685 patent/DE3931685A1/en not_active Withdrawn
-
1990
- 1990-08-07 EP EP19900115139 patent/EP0418534A3/en not_active Withdrawn
- 1990-09-07 JP JP23883190A patent/JPH03113291A/en active Pending
- 1990-09-19 CA CA 2025756 patent/CA2025756A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03113291A (en) | 1991-05-14 |
| DE3931685A1 (en) | 1991-04-04 |
| EP0418534A3 (en) | 1991-10-23 |
| EP0418534A2 (en) | 1991-03-27 |
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